EP0688977B1 - Behelfssteuerung für Getriebe bei Schaltfehlern - Google Patents

Behelfssteuerung für Getriebe bei Schaltfehlern Download PDF

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Publication number
EP0688977B1
EP0688977B1 EP95303388A EP95303388A EP0688977B1 EP 0688977 B1 EP0688977 B1 EP 0688977B1 EP 95303388 A EP95303388 A EP 95303388A EP 95303388 A EP95303388 A EP 95303388A EP 0688977 B1 EP0688977 B1 EP 0688977B1
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EP
European Patent Office
Prior art keywords
ratio
transmission
section
engagement
main
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EP95303388A
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English (en)
French (fr)
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EP0688977A2 (de
EP0688977A3 (de
Inventor
Kwok Wah Chan
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Eaton Corp
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Eaton Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/16—Inhibiting or initiating shift during unfavourable conditions, e.g. preventing forward reverse shift at high vehicle speed, preventing engine over speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/70—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for change-speed gearing in group arrangement, i.e. with separate change-speed gear trains arranged in series, e.g. range or overdrive-type gearing arrangements
    • F16H61/702—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for change-speed gearing in group arrangement, i.e. with separate change-speed gear trains arranged in series, e.g. range or overdrive-type gearing arrangements using electric or electrohydraulic control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • F16H2061/047—Smoothing ratio shift by preventing or solving a tooth butt situation upon engagement failure due to misalignment of teeth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
    • F16H2061/1208—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures with diagnostic check cycles; Monitoring of failures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
    • F16H2061/1224—Adapting to failures or work around with other constraints, e.g. circumvention by avoiding use of failed parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
    • F16H2061/1228—Fixing failures by repairing failed parts, e.g. loosening a sticking valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
    • F16H2061/1232—Bringing the control into a predefined state, e.g. giving priority to particular actuators or gear ratios
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
    • F16H2061/1256—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures characterised by the parts or units where malfunctioning was assumed or detected
    • F16H2061/1276—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures characterised by the parts or units where malfunctioning was assumed or detected the failing part is a friction device, e.g. clutches or brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2306/00—Shifting
    • F16H2306/20—Timing of gear shifts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/36—Inputs being a function of speed
    • F16H59/38—Inputs being a function of speed of gearing elements
    • F16H59/40—Output shaft speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/36—Inputs being a function of speed
    • F16H59/38—Inputs being a function of speed of gearing elements
    • F16H59/42—Input shaft speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/68—Inputs being a function of gearing status
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
    • F16H61/682—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings with interruption of drive
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S477/00—Interrelated power delivery controls, including engine control
    • Y10S477/906—Means detecting or ameliorating the effects of malfunction or potential malfunction
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19167—In series plural interchangeably locked nonplanetary units
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19251—Control mechanism
    • Y10T74/19256—Automatic
    • Y10T74/1926—Speed responsive

Definitions

  • the present invention relates to a control method and control system for shifting a compound semi-blocked, splitter-type automatic or semi-automatic transmission system.
  • Automatic and semi-automatic mechanical transmission systems are known in the prior art and illustrated in U.S. Pats. No. 4,361,060, 4,648,290 and 5,109,721.
  • Semi-blocked compound transmissions of the splitter type are known in the prior art and illustrated in U.S. Pats. No. 3,924,484; 4,735,109 and 4,736,643.
  • the present invention relates to a splitter section engagement fault control method/system for an automated compound semi-blocked mechanical transmission system wherein, upon sensing that the main section is engaged in the desired ratio thereof and that a known ratio other than the target ratio has engaged, will declare a splitter section fault and will adapt a splitter section fault mode of operation.
  • the splitter section ratio associated with the known ratio is the default splitter ratio, and further splitter section shifting is prohibited.
  • the shift control upon sensing that either the main section or the auxiliary section is engaged in the required ratio thereof for the transmission target gear ratio, and that the associated auxiliary section or main section ratio has not after a period of time engaged, the shift control will cause engagement of an allowable ratio in the auxiliary or main section and thereafter all ratio combinations including in combination the unengageable auxiliary section and main section ratio will not be allowed.
  • Fully automatic transmission systems both for heavy-duty vehicles such as heavy-duty trucks and/or coaches, and for automobiles, that sense throttle openings or positions, vehicle speeds, engine speeds, and the like, and automatically shift the vehicle transmission in accordance therewith are well known in the prior art.
  • Such fully automatic change gear automated mechanical transmissions utilizing electronic and/or pneumatic logic and actuators to engage and disengage mechanical (i.e ., positive) clutches to achieve a desired gear ratio. Examples of such transmissions may be seen by reference to U.S. Pats. No. 3,961,546; 4,081,065; 4,361,060; 4,569,255; 4,576,065; 4,595,986; and 4,576,263.
  • the semi-automatic control system prohibits engagement of a driver-selected higher ratio (i.e ., an upshift) that would cause the engine speed to decrease below the idle speed ( i.e ., would cause stalling and/or over-stressing at low speeds of the engine) and of a lower ratio (i.e ., a downshift) if such a change would cause overspeeding of the engine.
  • a driver-selected higher ratio i.e ., an upshift
  • a lower ratio i.e ., a downshift
  • a control method for shifting automatic and semi-automatic mechanical transmissions including semi-blocked, splitter-type compound transmissions wherein each shift, both simple (auxiliary section only) and compound (main and auxiliary section), involves shifting of the main transmission section to neutral to allow shifting of the blocked auxiliary section without requiring a crossing of synchronous of the preselected jaw clutch members, is disclosed in U.S. Pat. No. RE 32,591.
  • a shift control system/method for an automated splitter-type, semi-blocked transmission system of the type shifted to main section neutral during each ratio change which will sense splitter section engagement faults involving engagement of a ratio other than the target ratio, and upon sensing such a fault, will adapt a splitter section engagement fault degraded mode of operation in which the engaged splitter section ratio is the default splitter section ratio, and further splitter section shifting is prohibited or, alternatively, upon sensing that either the main section or the auxiliary section is engaged in the required ratio thereof for the transmission target gear ratio, and that the associated auxiliary section or main section ratio has not after a period of time engaged, the shift control will cause engagement of an allowable ratio in the auxiliary or main section and thereafter, all ratio combinations including in combination the unengageable auxiliary section and main section ratio, will not be allowed.
  • Figure 1 is a symbolic illustration of a splitter-type, semi-blocked automatic/semi-automatic mechanical transmission system.
  • Figure 2 is a symbolic illustration of control members and sensors of the system illustrated in Figure 1 .
  • Figures 3 and 3B illustrate the control and display console of the system illustrated in Figure 1 .
  • Figure 4 is a symbolic illustration of a "4 ⁇ 3" 12-speed compound splitter-type, semi-blocked transmission.
  • Figures 4A-4D are partial views of various components of the transmission of Figure 4 .
  • Figure 5 illustrates the typical shift pattern for the transmission of Figure 4 .
  • FIGS 6A and 6B are symbolic representations, in flow chart format, of the shift control of the present invention.
  • Figures 7A and 7B are symbolic representations, in flow chart format, of an alternate shift control of the present invention.
  • compound transmission is used to designate a change speed transmission having a main transmission portion and an auxiliary transmission portion connected in series whereby the selected gear reduction in the main transmission portion may be compounded by further selected gear reduction in the auxiliary transmission portion.
  • splitter-type compound transmission as used herein will designate a compound transmission wherein the auxiliary transmission is used to provide various selectable steps for subdivisions of the gear ratio selected in the main transmission portion.
  • the main transmission section is typically provided with relatively wide steps which are split or subdivided by the auxiliary section.
  • locked transmission or “blocked transmission section” shall designate a change gear constant mesh transmission or transmission section, wherein a selected one of a plurality of axially moveable gears is nonrotatably coupled to a shaft as aresult of axial movement of the selected gear from the neutral to the engaged position thereof, and by means of a resiliently biased positive clutch and a blocker is utilized to prevent such engagement until the members of the positive clutch are at substantially synchronous rotation, such synchronous condition achieved by manual and/or automatic manipulation of the transmission input and/or output shafts to cause a crossing of synchronous condition therebetween, but not typically achieved by frictional contact of the selected clutch members sufficient to cause one of the clutch members, and the apparatus associated therewith, to rotate with the other clutch member.
  • Blocked transmissions and/or transmission sections are illustrated in U.S. Pats. No. 3,799,002; 3,924,484; 4,192,196 and 4,440,037, and European Pat. No. 0,070,353.
  • the automatic or the semi-automatic control system of the present invention is particularly advantageously applied to a splitter-type compound transmission of the type having a non-synchronized, non-blocked main transmission section connected in series with an auxiliary section of the blocked splitter type.
  • Such transmissions are known in the prior art and are referred to as "semi-blocked" transmissions, and are described and illustrated in U.S. Pats. No. 4,735,109; 4,736,643; 4,930,078 and 5,042,327.
  • a driver-operated throttle 24 is sensed at sensor 22 and a signal indicative thereof (THD) fed to a central processing unit 38, which also receives inputs relative to engine speed from sensor 28 and/or transmission input shaft speed from sensor 32, transmission output shaft speed from sensor 36, and positive or negative actuations of the driver's gear shift lever, or "joy stick" 1, to be described in greater detail below.
  • TDD signal indicative thereof
  • a sensor 35 also may be provided to sense mainshaft speed which, in combination with sensor 36, will allow sensing if the auxiliary section of transmission 12 is engaged in a particular ratio.
  • Control logic circuits, sensors, and actuators for the transmission system 10 as disclosed in Figures 1 and 2 may be as disclosed in aforementioned U.S. Pats. No. 4,361,060 and 4,595,986.
  • central processing unit 38 receives inputs, processes same in accordance with predetermined logic rules, and provides command output signals to pneumatic and/or electrical actuators for control of an exhaust brake 17 and/or an input shaft brake 18 for rapid upshifts, and automatic fuel control 26 to "blip" or "dip” the supply of fuel to the engine 14 to achieve rapid synchronous rotation preparatory to a shift, clutch control via operator 30, and ratio shifting via transmission operator 34.
  • the central processing unit also sends command output signals to the display 2 to be described in greater detail below.
  • the automatic/semi-automatic transmission system 10 may additionally comprise a usual foot-operated manual clutch control 3 intended for use only for start from rest and/or low speed creeping maneuvering situations.
  • the control 38 receives signals indicative of manual clutch control 3 position and of actuation of the vehicle brakes 4.
  • the automatic/semi-automatic mechanical transmission system 10 also includes sources of electric and/or pneumatic power (not illustrated).
  • blip designates a temporary increase in the supply of fuel to the engine 14, while the term “dip” means a momentary decrease in supply of fuel to the engine.
  • the terms blip and dip are usually associated with automatic controller 38 commanded increases and decreases, respectively, of the supply of fuel to the engine independent of the operator selected position of manual throttle pedal 24.
  • the engine may be electronically controlled and may communicate with the controller 38 over an electronic datalink (DL) of the type conforming to the SAE J1922, SAE J1939 and/or CAN protocols.
  • DL electronic datalink
  • the central processing unit 38 may be contained in a box or housing 38A, which housing carries the display panel 2 having an upshift indicator display 2', a downshift indicator display 2'' and a currently engaged gear ratio display 2''', the shift select lever 1, an optional reverse enable button 1A, as well as a central processing unit electronic circuitry 38B.
  • the display 2 includes upshift indicator section 2', downshift indicator section 2'' and currently engaged gear ratio indicator section 2'''.
  • the currently engaged gear ratio display section 2''' is presently displaying a "6" indicating that the vehicle transmission is operating in sixth (6th) gear.
  • the upshift display section 2' has three lines indicating the maximum number of permissible consecutive upshifts permitted according to the sensed input parameters, such as sensed engine or input shaft speed and sensed output shaft speed as processed according to the predetermined logic rules or program. In the present situation, the three lines indicate that a single, a double or a triple upshift is permissible.
  • the driver may select apermissible shift directly to either seventh (7th), eighth (8th) or ninth (9th) speed.
  • the downshift display 2'' section has two lines indicating the maximum number of permissible consecutive downshifts permitted according to the sensed parameters as processed by the predetermined logic or program. In the present situation, the two lines in display 2' indicate that the transmission may be permissibly downshifted to either fifth (5th) or to fourth (4th) gear.
  • the permissibility of a possible upshift or downshift is determined by comparing the expected engine speed at the completion of such an upshift or downshift, at a determined or calculated vehicle speed and fully engaged master clutch, to a fixed range of maximum and minimum permissible engine speeds.
  • the central processing unit 38 will not issue command signals to execute a selected impermissible ratio change.
  • a central processing unit will execute the closest permissible ratio change to that selected by the operator.
  • the central processing unit 38 will issue command output signals for a double downshift from sixth gear to fourth gear.
  • Gear shifts are achieved without the operator manually engaging and/or disengaging the master clutch 16 by means of the mechanical manual clutch pedal 3.
  • Manual clutch pedal 3, if provided, is normally only used for starting from rest, reversing or for maneuvering, etc., as vehicle clutches have traditionally been used.
  • the driver moves lever 1 forward (for upshifts) and rearward (for downshifts) from the position illustrated in Figures 2 and 3 .
  • the operator will move lever 1 forward once and the lever will then return to the neutral or centered position under bias. If, in sixth gear as shown, the operator moves the lever forward three times in quick succession, each allowing its return to rest, he will skip two gears in effect, and achieve a skip shift directly into ninth speed ( i.e ., seventh and eighth speeds will not be engaged).
  • the declutching of the master clutch 16 and synchronizing of the selected jaw clutch member associated with the selected gear ratio is achieved automatically and rapidly due to automatic throttle and clutch control and braking of the input shaft and/or the engine.
  • the control system is semi-automatic and the driver must exercise his discretion as to when to up or downshift, and as to how many gear ratios to up or downshift, but is not called upon to coordinate gear lever, throttle pedal and clutch actuation. Once the driver has selected a permitted gear ratio, the throttle is blipped to achieve necessary synchronization during a downshift, or dipped for achieving necessary synchronization during an upshift, all of which is done automatically for the driver by the central processing unit 38.
  • the reverse mode of operation may be achieved only from the neutral at rest position and then is achieved by moving control lever 1 backwardly from the currently engaged neutral position.
  • a reverse button 1A may be provided which button must be depressed prior to the central processing unit interpreting a backward movement of the control lever 1 when in the neutral position as a request for reverse operation.
  • the transmission operator 34 includes an electro pneumatic ("EP") manifold is preferably broken down into two elements. The first associated with the front box and the second with back box operations.
  • the EP manifold is a manifold controlled by solenoid valves and associated with the cylinders carrying the shift pistons.
  • the main section control may be of the X-Y type as seen in U.S. Pat. No. 4,899,607.
  • the main section control 34 is provided with sensors 34A whereby the positioning of the shift forks may be sensed to sense the engaged ratio in the main section.
  • transmission 12 is a multi-speed transmission having at least five, preferably nine or more, selectable forward ratios.
  • the structure of a 12-forward-speed, splitter-type transmission 12, and of the blocked jaw clutch members utilized in the auxiliary transmission section of transmission 12, is known in the prior art and may be appreciated in greater detail by reference to above mentioned U.S. Pats. No. 3,799,002; 3,921,469; 3,924,848; 4,194,410; 4,440,037; 4,736,643 and 4,735,109.
  • transmission 12 inlcudes a main section 212 connected in series with a blocked splitter-type auxiliary section 214.
  • the transmission includes an input shaft 218 supported adjacent its rearward end by a bearing 220 and is provided with an input gear 222 nonrotatably connected thereto, as by splines.
  • the input gear 222 simultaneously drives a plurality of main section countershafts at equal speeds.
  • the transmission is provided with two main section countershafts, 224 and 226, disposed on diametrically opposite sides of the mainshaft 228, which mainshaft is coaxially aligned with the input shaft 218 and is provided with a pilot portion 230 on its forward end rotatably received within and supported by the rearward end of the input shaft 218.
  • the input shaft 218 is normally driven in one direction only by a primemover, such as a throttle controlled Diesel engine E through a selectively operated, normally engaged, friction master clutch C.
  • a primemover such as a throttle controlled Diesel engine E
  • a selectively operated, normally engaged, friction master clutch C
  • Each of the main section countershafts 224 and 226 is provided with an identical grouping ofcountershaft gears, such as the pair of gears 236, of identical size and number of teeth and disposed on diametrically opposite sides of the mainshaft 228.
  • a plurality of main section mainshaft drive gears 246, 248, 250 and 252 surround the mainshaft 228 and are selectably clutchable thereto, one at a time, by sliding clutch collars as is well known in the art.
  • the main section mainshaft gears 246, 248 and 250 encircle the mainshaft 228, are in continuous meshing engagement with, and are floatingly supported by the diametrically opposite pairs of countershaft gears, 238, 240 and 242, respectively, which mounting means and the special advantages resulting therefrom are explained in greater detail in U.S. Pats. No. 3,105,395 and 3,335,616.
  • the mainshaft gear 252 is the reverse gear and is in continuous meshing engagement with a pair of countershaft gears 244 by means of conventional intermediate idler gears (not shown).
  • the forwardmost countershaft gears 236 are continually meshed with and driven by the input gear 222 for causing simultaneous rotation of the countershafts 224 and 226 whenever the input shaft is rotatably driven.
  • Main section mainshaft gears 246, 248, 250 and 252; and main section countershaft gears 236, 238, 240, 242 and 244, and the idler gears, are all constantly meshed with and driven by the input gear 222 and thus, in combination, form the input gearing of the transmission 12.
  • various abutment rings 254 are provided to axially fix the main section mainshaft gears relative to mainshaft 228.
  • Sliding clutch collars 256, 258 and 260 are splined to mainshaft 228 for axial movement relative thereto and rotation therewith as is well known in the art.
  • Sliding clutch 256 is axially slidable by means of shift fork 262 to clutch gear 252 to the mainshaft.
  • Sliding clutch 258 is axially slidable by means of shift fork 264 to clutch either gear 250 or 248 to the mainshaft.
  • Sliding clutch 260 is axially slidable by means of shift fork 264 to clutch gear 246 to the mainshaft or to clutch the input gear 222 (and thus the input shaft 218) to the mainshaft.
  • Shift forks 262, 264 and 266 are attached to shift bars or rails of a known shift bar housing assembly.
  • the mainshaft 228 extends thereinto and is coaxially arranged with and piloted into an output shaft 274 which is in turn supported within the housing 216 by suitable bearings generally indicated at 276.
  • Said auxiliary section further includes a plurality of auxiliary section countershafts 278 and 280 each having an identical grouping of countershaft gears 284, 286 and 288 therein.
  • mainshaft section countershafts, 224 and 226, are displaced about 90° from the auxiliary section countershafts.
  • Main section countershafts are supported in housing 216 by bearings 290 and 292 while auxiliary section countershafts 278 and 280 are supported in housing 216 by bearings 294 and 296.
  • auxiliary section mainshaft gears 308 and 310, encircle the mainshaft 228 and are constantly meshed with and floatingly supported by the auxiliary countershaft gear pairs 284 and 286, respectively.
  • Output gear 312 is splined to output shaft 274 for axial movement relative thereto and rotational movement therewith.
  • Output gear 312 is constantly meshed with auxiliary countershaft gear pair 288.
  • Resiliently biased clutch members 316, 318 and 320 are splined to mainshaft 228 and, in combination with blockers (not shown) provide resilient, blocked clutching apparatus of the type described in above-mentioned U.S. Pats. No. 3,799,002, 3,921,469; 3,924,484 and 4,736,643 for selectively clutching gears 308, 310 and 312, respectively, one at a time, to mainshaft 228.
  • Clutch 316 is biased axially by spring 330 and limited in its axial movement by positive stop 334.
  • Clutch members 318 and 320 are biased axially apart by spring 138 surrounding the mainshaft and limited in axial movement by stops 338 and 340.
  • Gear 312 is axially moved by shift fork 342 and gears 308 and 310 are joined for joint axial movement and independent rotation by ring 346 and are axially movable by shift fork 348.
  • Gears 308, 310 or 312 are selectively engaged, one at a time, to mainshaft 228.
  • engagement of gear 312 to the mainshaft 228 is effective to couple mainshaft 228 directly to the output shaft 274.
  • the shift pattern for transmission 12 is symbolically illustrated in Figure 5.
  • the yieldable blocked jaw clutch structures are arranged between the shiftable mainshaft gears and the auxiliary section and are provided with resilient meansfor urging engagement thereof as set forth in detail in the above-mentioned U.S. Pat. No. 3,799,002; 3,924,484 and 3,983,979. While clutch means utilizing relatively nondeformable blockers of the prior art are not identical with each other, they are generally similar and hence insofar as the present invention is concerned, it will be sufficient to described only one of them in detail with the understanding that same may be applied to the other clutch units without difficulty by anyone skilled in the art.
  • said jaw clutch unit is generally designated 356 and includes an annular clutch collar or clutch member 316 encircling the mainshaft 228.
  • the clutch collar 316 is provided with internal splines 358 which are disposed within corresponding external splines 360 provided on the mainshaft 228 for interconnecting the clutch collar 316 to the mainshaft 228 for rotation therebetween.
  • the cooperating splines 358 and 360 permit the clutch collar 316 to freely slide axially relative to the shaft 228.
  • Other means for mounting clutch collar 316 to mainshaft 228 allowing relative axial but not rotational motion therebetween may be utilized.
  • a stop ring 334 is seated within a suitable groove formed on the external periphery of the shaft 228 and is disposed for contacting the clutch collar 316 and limiting the rightward axial movement thereof.
  • the collar 316 is normally resiliently urged by means of a spring 330 into a butting engagement with the stop ring 334.
  • the clutch collar 316 is provided with external teeth 362 thereon which are adapted to meshingly engage the internal teeth 364 provided on the mainshaft gear 308.
  • the internal teeth 364 form the other jaw clutch member of clutch assembly 356.
  • the teeth 362 on the clutch collar 316 are tapered, as at 366 and in a similar manner the leading edge of the teeth 364 on the mainshaft gear 308 are similarly tapered at 368.
  • the tapered conical surfaces each extend at an angle of preferably between 30° and 40° relative to the longitudinal axis of the mainshaft 228. The exact degree of taper, and the advantages, thereof, are explained in detail in U.S. Pat. No. 3,265,173.
  • the other end of the spring 330 resiliently acts against a spring seat member 369 fixed to mainshaft 228.
  • a selected number, here three, of the teeth 362 are partially removed for permitting the presence of a blocking ring as hereinafter further described. Such partial removal leaves, however, an axially shortened or partially removed tooth 370 for cooperation with the blocking ring.
  • relatively nondeformable blockers also called blocker rings, blocking rings and sensors; one thereof is indicated generally at 324, and comprises a ring encircling the clutch member 316 and has an appropriate number, here three pairs, of radially inward projections 372 and 374, which when properly positioned will mate with the external teeth above mentioned.
  • the inward projections or teeth 384 and 376 are contoured at their sides to lie snugly against the adjacent ones of the teeth 362, are positioned to project into the spaces between a partially removed tooth 370 and the teeth 362 on each side thereof.
  • Each pair of projections 372 and 374 are circumferentially of less dimension than the corresponding circumferential spaces defined by partially removing teeth 370 and thus blocker ring 324 may be rotated in either a limitedclockwise or counterclockwise direction relative to clutch member 316 from the position seen in Figure 4B in which the space between teeth 372 and 374 aligns with partially removed tooth 370.
  • Contact of either blocker tooth 372 or 374 by a clutch tooth 362 will limit such relative rotation and cause blocker 324 to rotate with clutch member 316.
  • the space between the inwardly projecting teeth 372 and 374 is, however, of a clearance distance wider than the corresponding circumferential dimension of the tooth 370 so that when properly aligned at synchronism (or more accurately, when the relative speeds of the clutch components cross synchronism) the teeth 372 and 374 will straddle the tooth 370 and the clutch member 320 can move axially through but not past blocker ring 324 to effect engagement with its corresponding gear.
  • the end faces of the blocker teeth 372 and 374 are tapered as at 376 and 378.
  • the end face of partially removed tooth 270 is also preferably provided with tapers to ramps 380 and 382 complementary with the tapers or ramps l78 and 180 on the blocker ring blocking teeth 372 and 374.
  • the angles 383 of the ramps 376, 378, 380 and 382 is selected such that the blocking teeth and the partially removed teeth will remain in proper blocked position when the main transmission section 212 is engaged but will tend, under a contacting force, if an auxiliary section shift has been selected, to cause the blocker and clutch to assume a nonblocking position (by causing relative rotational movement of the clutch 316, blocker 324 and/or mainshaft 228) if the main transmission section is disengaged ( i.e ., in neutral).
  • a ramp angle 382 of about l5° - 25°, preferably about 20°, relative to a plan P normal to the axis of rotation of the mainshaft 226 has proven highly satisfactory for most known semi-blocked transmission structures.
  • the radially inner side of ring 324 may be provided with an inwardly directed groove 384 which receives an annual resilient ring 386 which is normally of slightly less internal diameter than the external diameter of the teeth 362 so that when the parts are in the assembled condition, ring 386 is distorted slightly outwardly thereby to exert a light but definite pressure against the external surface of said teeth 362.
  • the ring 386 fits loosely and only in light frictional contact with the walls of the groove 384, this effects a significant resistance to axial movement between the blocker ring 126 and the clutch ring 316 but only an insignificant resistance to relative rotative movement therebetween.
  • a suitable conical surface 388 projects radially outwardly from the blocker ring 324 and is positioned for engagement with a similar conical surface 390 on a radially inner wall of the gear 308.
  • the axial drag above mentioned is sufficient that the rotative driving effect of the surface 390 onto the blocker 324 is much greater than whatever rotative resistance may exist between the blocker 324 and the clutch member 314.
  • a stop ring 392 limits movement of the blocker 324 away front the conical surface 390 when the clutch ring 316 moves out of engagement (leftwardly in Figure 4A ).
  • the ratio must be preselected and then the associated sensor must be moved to a nonblocking position. This is accomplished in one of two ways; either the rotational speed of the mainshaft 228 is manipulated to cause a reversal of the relative rotation of the clutch members ( i.e ., a crossing of synchronous) or the mainsection is shifted into neutral,lowering the inertia on the mainshaft 228 which allows the sensor unblocking ramps, 376 and 378, to rotate the mainshaft to a nonblocking position.
  • a transmission ratio (GR) for transmission 12 is defined by a main section (212) ratio multiplied by an auxiliary section (214) ratio.
  • the main section (212) is preferably shifted to neutral, the blocked jaw clutch assembly associated with the required splitter ratio in the splitter section (214) is preselected and then the appropriate main section ratio is engaged, using throttle blip and/or engine braking as necessary. Engagement of the main section in the desired main section ratio may be reliably sensed by position sensors 34A. However, position sensors, if any, associated with the auxiliary section actuator will only indicate a preselected position, not necessarily an engaged position, of the selected auxiliary section clutch assembly.
  • a shift from sixth (6th) to seventh (7th) will require clutch 258 disengaging gear 248 from mainshaft 228, disengaging clutch 320 and preselecting clutch 316 in the auxiliary section 214 and then engaging gear 246 to the mainshaft 228 by clutch 260. It is expected that preselected clutch 316 will engage splitter gear 308 to the mainshaft under the action of the sensor unblocking ramps as the mainshaft is at a relatively low inertia while in neutral.
  • an input signal indicative of the axial position of shift fork 266 and/or jaw clutch 260 is a reliable indication of engaged or not engaged condition of gear 246 while signals, if any, indicative of the axial positioning of shift fork 348 and/or gear 308 are only indicative of preselection of engagement of gear 308 to mainshaft 228 by blocked jaw clutch 316.
  • a technique is provided to confirm engagement of a target ratio, to take corrective action if non-engagement of the target ratio is simply a blocker hang-up and, if this corrective action is not effective, to implement engagement fault degraded modes of operation.
  • the target ratio is eighth (8th) and IS/OS shows seventh (7th) is engaged, then the system will command to shift into seventh (7th) again, and once the shift has completed, the current splitter ratio will be locked (i.e., other splitter ratios will not be available because there may be mechanical failures in the splitter unit).
  • splitter 1 lower splitter
  • the available gears will be 1R, N, 1, 4, 7 and 10 (main box shift only).
  • the engine is fueled with the main section and the master clutch remaining engaged to cause the input shaft rotational speed to equal or exceed the synchronous speed thereof (i.e., IS ⁇ OS * GR T ) and then the engine is defueled to cause input speed to be below synchronous speed, which will cause the suspected hung-up blocked jaw assembly to pass through synchronous, which should knock the blocker off the blocked position thereof.
  • This routine is rather quick and does not require a recycling of the complete shift routine.
  • auxiliary section 214 does not engage and/or cannot be caused to engage for a period of time (such as 10-15 seconds)
  • auxiliary section intermediate or high to engage i.e ., gears 310 or 312 to engage mainshaft 228, and thereafter all combinations including auxiliary section low (i.e ., 1st, 4th, 7th and 10th) will not be allowable.
  • a control is provided for an automated, compound, semi-blocked, splitter-type transmission which will sense for splitter section engagement faults or splitter section or main section faults and, upon sensing such a fault, will adopt an appropriate fault-tolerant mode of operation.

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Claims (11)

  1. Steuerverfahren für ein automatisches mechanisches Getriebesystem (10), welches folgendes aufweist:
    einen brennstoffgesteuerten Motor (14) und ein Gruppen-Gangwechselgetriebe (12) mit Konstanteingriff, und zwar einen Hauptgetriebeabschnitt (212) und einen aufspaltblockierten Hilfsgetriebeabschnitt (214) verbunden in Serie damit, aufweisend wobei der Hauptabschnitt (212) Sensoren (32) aufweist zum Liefern von Eingangssignalen, welche eine Anzeige bilden für den Eingriffszustand des Hauptabschnitts (212),
    wobei das Getriebe (12) eine Vielzahl von bekannten Übersetzungsverhältnissen (GR) definiert, und zwar jedes definiert durch eine einzigartige Kombination des Eingriffs eines bestimmten Hauptabschnitt (212)-Verhältnisses und eines bestimmten Hilfsabschnitts (214)-Verhältnisses,
    wobei das System ferner Hauptabschnitt (212)- und Hilfsabschnitt (214)-Schaltmittel aufweist,
    eine zentrale Verarbeitungseinheit (38 (i) zum Empfang von Eingangssignalen, (ii) zur Bestimmung eines Soll-Übersetzungsverhältnisses (GR) durch Verarbeiten der Eingangssignale entsprechend einem Programm und (iii) zur Erzeugung von Befehlsausgabesignalen für die Schaltmittel, wobei die Verarbeitungseinheit (38) Änderungen des Übersetzungsverhältnisses (GR) in ein Zielverhältnis (GRT) in der Folge befiehlt, und zwar aufweisend als erstes das Befehlen des Schaltens des Hauptgetriebeabschnitts (212) in Neutral und sodann Befehlen einer Schaltung im Hilfsgetriebeabschnitt (214) zum Eingriff mit einem erforderlichen Hilfsabschnitt (214)-Verhältnis und darauf Befehlen einer Schaltung des Hauptgetriebeabschnitts (212) zum Eingriff eines angeforderten Verhältnisses der Hauptabschnitt (212)-Verhältnisse, wobei das Verfahren dadurch gekennzeichnet das bei Vollendung des befohlenen Eingriffs des Hauptabschnitts (212) in das angeforderte Verhältnis folgendes vorgesehen ist:
    (a) Bestätigung des Eingriffs des Hauptabschnitts (212) in dem erforderlichen Verhältnis davon;
    (b) sodann Abfühlen der Bestätigung des Eingriffs des Getriebes (12) in dem Zielverhältnis (GRT);
    (c) sodann, wenn das Getriebe (12) nicht als in Eingriff mit dem Zielverhältnis (GRT) stehend bestätigt wird, Abfühlen der Bestätigung des Eingriffs des Getriebes (12) in irgendeinem Getriebeverhältnis (GR);
    (d) sodann, wenn das Getriebe (12) als in Eingriff in einem Übersetzungsverhältnis (GR) anders als dem Zielverhältnis (GRT) als in Eingriff stehend bestätigt wird, (i) Erklären eines Hilfsabschnitts (214)-Eingriffsausfalls, (ii) Zurückhalten des Hilfsabschnitts (214)- in dem derzeit in Eingriff stehenden Hilfsanschnitt (214)-Verhältnis davon und (iii) Gestatten der Schaltung des Hauptgetriebeabschnitts (212)-, aber nicht des Hilfsabschnitts (214)-Verhältnisses.
  2. Verfahren nach Anspruch 1, wobei das Getriebe (12) eine Antriebswelle (218) und eine Abtriebswelle (274) aufweist, wobei die Eingangssignale Signale aufweisen, die eine Anzeige der Drehzahl oder Drehgeschwindigkeit der Antriebswelle (IS) (218) und der Abtriebswelle (OS) (274) vorsehen, und der Eingriff abgefühlt wird, wenn IS = (OS*GR)+K ist, wobei:
    GR ein numerisches Zahnradverhältnis und
    K der Toleranzfaktor ist.
  3. Verfahren nach Anspruch 2, wobei der Wert von K ungefähr 50 - 150 Umdrehungen pro Minute beträgt.
  4. Steuersystem für ein automatisches mechanisches Getriebesystem (10) mit einem brennstoffgesteuertem Motor (14) und einem Wechselganggetriebe (12) der Verbindungssplitbauart (Gruppenbauart) mit konstantem Eingriff, wobei das Getriebe (12) einen Hauptgetriebeabschnitt (212) und einen Hilfsgetriebeabschnitt (214), der blockierten Splitbauart aufweist, und zwar verbunden in Serie mit dem Hauptgetriebeabschnitt, wobei der Hauptgetriebeabschnitt (212) Sensoren (32) aufweist, um Eingangssignale zu liefern, die eine Anzeige für den Eingriffszustand des Hauptabschnitts (212) bilden, wobei das Getriebe (12) eine Vielzahl von bekannten Übersetzungsverhältnissen (GR) definiert, und zwar jedes definiert durch eine einzigartige Kombination des Eingriffs eines bestimmten Hauptabschnitts (212)-Verhältnisses und eines bestimmten Hilfsabschnitts (214)-Verhältnisses, wobei das System ferner Hauptabschnitts (212)- und Hilfsabschnitts (214)-Schaltmittel aufweist, eine zentrale Verarbeitungseinheit (38) um (i) Eingangssignale zu empfangen, (ii) ein Soll-Übersetzungsverhältnis (GR) zu bestimmen, und zwar durch Verarbeitung der Eingangssignale entsprechend einem Programm, und (iii) zur Erzeugung von Befehlsausgangssignalen für die Schaltmittel, wobei die Verarbeitungseinheit (38) alle Nichtrichtungsänderungen in dem Übersetzungsverhältnis (GR) in ein Zielverhältnis (GRT) befiehlt, und zwar in der Folge, welche folgendes aufweist: als Erstes Befehlen des Schaltens des Hauptgetriebeabschnitts (212) in Neutral, sodann Befehlen einer Schaltung des Hilfsgetriebeabschnitts (214) zum Eingriff mit einem erforderlichen Hilfsabschnitts (214)-Verhältnis, und sodann Befehlen einer Schaltung in dem Hauptgetriebeabschnitt (212) zum Eingriff mit einem der Hauptabschnitts (212)-Verhältnisse,
    wobei das Steuersystem gekennzeichnet ist durch Mittel, die bei Vollendung des Befehlseingriffs des Hauptabschnitts (212) in das dafür erforderliche Verhältnis effektiv sind, um:
    (a) den Eingriff des Hauptabschnitts (212) in das erforderliche Verhältnis davon zu bestätigen;
    (b) sodann Abfühlen, zur Bestätigung des Eingriffs des Getriebes (12) in dem Zielverhältnis (GRT);
    (c) sodann, wenn das Getriebe (12) nicht als in Eingriff stehend mit dem Zielverhältnis (GRT) bestätigt wird, Abfühlen der Bestätigung des Eingriffs des Getriebes (12) in irgendeinem Getriebeverhältnis (GR);
    (d) sodann, wenn das Getriebe (12) als in Eingriff stehend mit einem Übersetzungsverhältnis (GR) anders als dem Zielverhältnis (GRT) stehend bestätigt ist, (i) Erklären eines Hilfsabschnitts (214)-Eingriffsfehlers, (ii) Halten des Hilfsabschnitts in dem derzeit in Eingriff stehenden Hilfsabschnitt (214)-Verhältnis davon und (iii) Gestatten des Schaltens des Hauptgetriebeabschnitts (212) aber nicht des Hilfsabschnitts (214)-Verhältnisses.
  5. System nach Anspruch 4, wobei das Getriebe (12) eine Antriebswelle (218) oder eine Abtriebswelle (274) aufweist, wobei die Eingangssignale Signale aufweisen, die eine Anzeige für die Drehgeschwindigkeit oder Drehzahl der Antriebswelle (IS) (18) und der Abtriebswelle (OS) (274) bilden und der Eingriff abgefühlt wird, wenn IS = (OS*GR)+K ist, wobei:
    GR ein numerisches Zahnrad- oder Getriebeverhältnis ist und
    K ein Toleranzfaktor ist.
  6. System nach Anspruch 5, wobei der Wert von K ungefähr 50 - 150 Umdrehungen pro Minute ist.
  7. Steuerverfahren für ein automatisiertes mechanisches Getriebesystem (10), wobei folgendes vorgesehen ist: Ein brennstoffgesteuerter Motor (14) und ein Wechselgetriebe (12) der Verbundsplitkonstanteingriffbauart, und zwar einen Hauptgetriebeabschnitt (212) und einen Hilfsgetriebeabschnitt (214), der blockierten Splitbauart aufweisend, und zwar verbunden in Serie damit, Sensoren (32) zum Liefern von Eingangssignalen unabhängig eine Anzeige bildend für den Eingriffszustand des Hauptabschnitts (212) und des Hilfsabschnitts (214), wobei das Getriebe (12) eine Vielzahl von bekannten Übersetzungsverhältnissen (GR) definiert, von denen jedes durch eine einzigartige Kombination des Eingriffs eines bestimmten Hauptabschnitts (212)-Verhältnisses und eines bestimmten Hilfsabschnitts (214)-Verhältnisses definiert ist,
    wobei das System ferner Hauptabschnitts (212)- und Hilfsabschnitts (214)-Schaltmittel aufweist, eine zentrale Verarbeitungseinheit (38), um (i) Eingangssignale zu empfangen, (ii) das Soll-Übersetzungsverhältnis (GR) bestimmen durch Verarbeitung der Eingangssignale gemäß einem Programm und (iii) zur Erzeugung von Befehlsausgangssignalen für die Schaltmittel, wobei die Verarbeitungseinheit (38) Änderungen des Übersetzungsverhältnisses (GR) befiehlt, und zwar in ein Zielverhältnis (GRT) in der Sequenz, die folgendes aufweist: Zuerst Befehlen des Schaltens des Hauptgetriebeabschnitts (212) in Neutral, sodann Befehlen einer Schaltung des Hilfsgetriebeabschnitts (214) zum Eingriff mit einem erforderlichen Hilfsabschnitt (214)-Verhältnis und sodann Befehlen einer Schaltung in dem Hauptgetriebeabschnitt (212) zum Eingriff eines erforderlichen Hauptabschnitts (212)-Verhältnisses, wobei das Verfahren, bei Vollendung des Befehlseingriffs des Hauptabschnitts (212) in das erforderliche Verhältnis davon und des Hilfsabschnitts (214) in das erforderliche Verhältnis davon gekennzeichnet ist durch
    (i)(a) Abfühlen des Eingriffs des Hauptabschnitts (212) in dem erforderlichen Verhältnis davon,
    (i)(b) bei Bestätigung des Eingriffs des Hauptabschnitts (212) in dem erforderlichen Verhältnis davon, sodann Abfühlen der Bestätigung des Eingriffs des Getriebes (12) in dem Zielverhältnis (GRT),
    (i)(c) sodann, wenn das Getriebe (10) als nicht in Eingriff in dem Zielverhältnis (GRT) stehend nach einer voreingestellten Zeitperiode bestimmt wird, Veranlassen des Eingriffs des Hauptabschnitts (212) in einem Verhältnis desselben anders als das des Hauptabschnitts (212)-Verhältnisses erforderlich für das Zielgetriebeverhältnis und Ungültigerklären zukünftiger Zielgetriebeverhältnisse aller Übersetzungsverhältnisse (GR) einschließlich in Kombination des Hauptabschnitts (212)-Verhältnisses erforderlich für das Zielverhältnis (GRT).
  8. Verfahren nach Anspruch 7, wobei das Getriebe (12) eine Antriebswelle (218) und eine Abtriebswelle (274) aufweist, wobei die Eingangssignale Signale aufweisen, welche die Drehzahl der Antriebswelle (IS) (218) und der Abtriebswelle (OS) (274) angeben, und wobei der Zielverhältniseingriff abgefühlt wird, wenn IS = (OS*GR)+K ist, wobei:
    GR ein numerisches Getriebeverhältnis und
    K ein Toleranzfaktor ist.
  9. Verfahren nach Anspruch 8, wobei der Wert von K ungefähr 50 -150 Umdrehungen pro Minute ist.
  10. Verfahren nach Anspruch 8, wobei das Getriebe (12) eine Hauptwelle (MS) (228) aufweist, wobei die Eingangssignale Signale (35) aufweisen, welche eine Anzeige der Drehzahl der Hauptwelle (MS) (228) und des Hilfsabschnitts (214)-Eingriffs sind, abgefühlt, wenn MS = (OS*GRAUX)+K, wobei:
    GRAUX ein numerisches Hilfsabschnittsgetriebeverhältnis ist.
  11. Steuersystem für ein automatisiertes mechanisches Getriebesystem (10) mit einem brennstoffgesteuerten Motor (14) und einem Wechselganggetriebe (12) der Compound-Splitter-Bauart mit konstantem Eingriff, wobei das Getriebe (12) einen Hauptgetriebeabschnitt (212) und einen blockierten Splittertyp-Hilfsgetriebeabschnitt (214) verbunden in Serie damit aufweist, ferner mit Sensoren (32) zum Vorsehen von Eingangssignalen, die unabhängig eine Anzeige bilden vom Eingriffszustand des Hauptabschnitts (212) und des Hilfsabschnitts (214),
    wobei das Getriebe (12) eine Vielzahl von bekannten Übersetzungsverhältnissen (GR) definiert, wobei jedes durch eine einzigartige Kombination des Eingriffs eines bestimmten Hauptabschnitts (212)-Verhältnisses und eines bestimmten Hilfsabschnitts (214)-Verhältnisses definiert ist,
    wobei das System (10) ferner Hauptabschnitts (212)- und Hilfsabschnitts (214)-Schaltmittel aufweist, eine zentrale Verarbeitungseinheit (38)
    (i) zum Empfang von Eingangssignalen,
    (ii) zur Bestimmung eines gewünschten Übersetzungsverhältnisses (GR) durch Verarbeitung der Eingangssignale entsprechend einem Programm, und
    (iii) zur Erzeugung von Befehlsausgangssignalen für die Schaltmittel, wobei die Verarbeitungseinheit (38) Änderungen im Übersetzungsverhältnis (GR) in ein Zielverhältnis (GRT) in der Folge befiehlt, wobei folgendes vorgesehen ist: Zuerst Befehlen des Schaltens des Hauptgetriebeabschnitts (212) in Neutral, sodann Befehlen einer Schaltung des Hilfsgetriebeabschnitts (214) zum Eingriff mit einem erforderlichen Hilfsabschnitt (214)-Verhältnis und sodann Befehlen einer Schaltung des Hauptgetriebeabschnittes (212), um eines der erforderlichen Hauptabschnitts (212)-Verhältnisse in Eingriff zu bringen,
    wobei das Steuersystem gekennzeichnet ist durch Mittel, die bei Vollendung des Befehlseingriffs des Hauptabschnitts (212) in das erforderliche Verhältnis davon und des Hilfsabschnitts (214) in das erforderliche Verhältnis folgendes bewirken:
    (i)(a) Abfühlen des Eingriffs des Hauptabschnitts (212) in das erforderliche Verhältnis davon,
    (i)(b) nach Bestätigung des Eingriffs des Hauptabschnitts (212) in dem erforderlichen Verhältnis davon sodann Abfühlen der Bestätigung des Eingriffs des Getriebes (12) in dem Zielverhältnis (GRT),
    (i)(c) sodann, wenn das Getriebe (10) nicht als im Zielverhältnis (GRT) nach einer vorbestimmten Zeitperiode in Eingriff stehend bestätigt wird, bewirken, daß der Hilfsabschnitt (214) in einem Verhältnis in Eingriff kommt, welches sich von dem Hilfsabschnitt (214)-Verhältnis unterscheidet, welches erforderlich ist für das Zielgetriebeverhältnis und Ungültigerklären zukünftiger Zielgetriebeverhältnisse aller Übersetzungsverhältnisse (GR) einschließlich der Kombination des Hilfsabschnitts (214)-Verhältnissse erforderlich für das Zielverhältnis (GRT); und
    (ii)(a) Abfühlen auf Eingriff des Hilfsabschnitts (214) in dem erforderlichen Verhältnis davon,
    (ii)(b) nach der Bestätigung des Eingriffs des Hilfsabschnitts (214) in dem erforderlichen Verhältnis davon sodann Abfühlen hinsichtlich Bestätigung des Getriebes (12) in dem Zielverhältnis (GRT),
    (ii)(c) sodann, wenn das Getriebe (12) als nicht im Eingriff im Zielverhältnis (GRT) nach einer vorbestimmten Zeitperiode befindlich bestätigt wird, Veranlassen, daß der Hauptabschnitt (212) in einem Verhältnis in Eingriff kommt, welches sich von dem Hauptabschnitts (212)-Verhältnis unterscheidet, welches für das Zielgetriebeverhältnis erforderlich ist, und Ungültigerklären der Zielgetriebeverhältnisse aller Übersetzungsverhältnisse (GR) einschließlich in Kombination mit dem Hauptabschnitt (212)-Verhältnis erforderlich für das Zielverhältnis (GRT).
EP95303388A 1994-06-25 1995-05-22 Behelfssteuerung für Getriebe bei Schaltfehlern Expired - Lifetime EP0688977B1 (de)

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GB9412805 1994-06-25
GB9412805A GB9412805D0 (en) 1994-06-25 1994-06-25 Engagement fault degraded mode control

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EP0688977A2 EP0688977A2 (de) 1995-12-27
EP0688977A3 EP0688977A3 (de) 1996-09-18
EP0688977B1 true EP0688977B1 (de) 2000-03-22

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CA2151631C (en) 1999-11-16
CN1116167A (zh) 1996-02-07
DE69515732T2 (de) 2000-11-09
KR100274962B1 (ko) 2000-12-15
US5537894A (en) 1996-07-23
DE69515732D1 (de) 2000-04-27
KR960001561A (ko) 1996-01-25
ES2144573T3 (es) 2000-06-16
JPH0849763A (ja) 1996-02-20
ATE191069T1 (de) 2000-04-15
GB9412805D0 (en) 1994-08-17
CA2151631A1 (en) 1995-12-26
EP0688977A2 (de) 1995-12-27
EP0688977A3 (de) 1996-09-18

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